WO2016015682A1 - 便于切换的可超越式传动装置 - Google Patents

便于切换的可超越式传动装置 Download PDF

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Publication number
WO2016015682A1
WO2016015682A1 PCT/CN2015/085969 CN2015085969W WO2016015682A1 WO 2016015682 A1 WO2016015682 A1 WO 2016015682A1 CN 2015085969 W CN2015085969 W CN 2015085969W WO 2016015682 A1 WO2016015682 A1 WO 2016015682A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
shaft
card
transmission
translatable
Prior art date
Application number
PCT/CN2015/085969
Other languages
English (en)
French (fr)
Inventor
冉庚枢
Original Assignee
重庆双庆产业集团有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 重庆双庆产业集团有限公司 filed Critical 重庆双庆产业集团有限公司
Priority to US15/329,687 priority Critical patent/US20170219074A1/en
Priority to EP15826636.1A priority patent/EP3176067A4/en
Priority to AP2017009789A priority patent/AP2017009789A0/en
Priority to EA201700092A priority patent/EA201700092A1/ru
Priority to MX2017001443A priority patent/MX2017001443A/es
Publication of WO2016015682A1 publication Critical patent/WO2016015682A1/zh
Priority to PH12017500187A priority patent/PH12017500187A1/en
Priority to CONC2017/0002077A priority patent/CO2017002077A2/es

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/048—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with parts moving radially between engagement and disengagement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H2003/0822—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the arrangement of at least one reverse gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3093—Final output elements, i.e. the final elements to establish gear ratio, e.g. dog clutches or other means establishing coupling to shaft

Definitions

  • the present invention relates to a transmission device, and more particularly to a translatable transmission device that facilitates switching.
  • the transmission device is an intermediate device that transmits the power of the power unit to a working mechanism or the like.
  • the basic function of the transmission device is to transmit the power generated by the engine to the driving wheels of the motor vehicle to generate a driving force, so that the motor vehicle can drive at a certain speed.
  • a transmission for steering switching in an existing motor vehicle includes an output gear 1, a drive gear 2, and a reverse gear set 3.
  • the output gear 1 is connected to a differential (not shown) and can be rotated in the forward direction and reversely to achieve forward and backward travel of the motor vehicle.
  • the driving gear 2 is connected to the driving shaft 4, and the driving shaft 4 is connected to an engine output shaft (not shown).
  • the driving gear 2 can be rotated by the driving shaft 4 to provide original power for the rotation of the output gear 1.
  • the driving gear 2 can also be connected to the fork lever 6 in the shifting device via the fork plate 5, and the driving gear 2 can be axially moved on the driving shaft 4 by the shifting lever 6 to respectively output
  • the gear 1 and the reverse gear set 3 are meshed to achieve forward and reverse rotation of the output gear 1, that is, forward and backward travel of the vehicle.
  • One end of the reverse gear set 3 is disposed close to the output gear 1, and is always in meshing engagement with the output gear 1, and the other end is disposed away from the output gear 1, and is in a position capable of meshing with the drive gear 2, and the reverse gear set enables The output gear 1 achieves a reverse rotation.
  • the shifting device (not shown) is operated, so that the fork lever 6 in the shifting device drives the driving gear 2 to move toward the output gear 1 through the fork plate 5, and The driving gear 2 is caused to mesh with the output gear 1.
  • the output gear 1 can be rotated forward under the driving of the driving gear 2, so that the vehicle is in the forward state.
  • the shifting device (not shown) is operated, so that the fork lever 6 in the shifting device drives the driving gear 2 to face away from the output gear 1 through the fork plate 5 Moving and causing the drive gear 2 to mesh with one end of the reverse gear set 3.
  • the output gear 1 can be reversely rotated by the driving gear 2 and the reverse gear set 3, so that the vehicle is in the reverse state.
  • the transmission device for fast and slow switching in the prior art vehicle includes a drive shaft 21, an output shaft 25, and two sets of transmission gear sets (fast drive gear set and slow drive gear set).
  • the fast drive gear set includes a fast drive gear 24 sleeved on the drive shaft 21 and a fast driven gear 27 sleeved on the output shaft 25.
  • the fast drive gear 24 and the fast driven gear 27 mesh with each other;
  • the gear set includes a slow drive gear 22 sleeved on the drive shaft 21 and a slow driven gear 26 sleeved on the output shaft 25, the slow drive gear 22 and the slow driven gear 26 meshing with each other.
  • a dial 23 is further disposed on the drive shaft 21 between the slow drive gear 22 and the fast drive gear 24.
  • the slow drive gear 22 and the fast drive gear 24 are respectively formed with a coupling hole, and the dial 23 is formed with a coupling claw.
  • the dial 23 can also be connected to a fork lever (not shown) in the shifting device through a fork plate (not shown). Under the driving of the fork lever, the dial 23 can be on the drive shaft 21 The upper axial movement is combined with the slow drive gear 22 and the fast drive gear 24, respectively, to achieve slow rotation and rapid rotation of the output shaft 25, that is, slow and fast travel of the motor vehicle.
  • the shifting device (not shown) is operated such that the shift lever in the shifting device moves the shifting wheel 23 toward the slow driving gear 22 through the fork plate. And the combination claw on the dial 23 is combined with the coupling hole on the slow drive gear 22. Thereby, the output shaft 25 can be rotated by the drive shaft 21, the slow drive gear 22 and the slow driven gear 26, so that the vehicle is in a slow running state.
  • the shifting device (not shown) is operated, so that the fork lever in the shifting device moves the dial wheel 23 toward the fast driving gear 24 through the fork plate, and The coupling pawl on the dial 23 is urged to engage the coupling aperture on the quick drive gear 24.
  • the output shaft 25 can be rotated by the drive shaft 21, the fast drive gear 24 and the fast driven gear 27, so that the vehicle is in a fast running state.
  • the motor vehicle requires the driving gear 2 to be close to and mesh with the output gear 1 during the forward and reverse switching, or the driving gear is required.
  • 2 Close to and engage with one end of the reverse gear set 3 to realize the switching of the forward and backward travel of the motor vehicle, and the misalignment sliding into the mesh between the gears often occurs because the diameters of the two gears are too large. Cross collision and blockage, which can cause the gears to slip into the meshing properly, which will make the switching failure, and may even cause the gear to be damaged;
  • a translatable transmission device for facilitating switching comprising a transmission gear and a transmission shaft disposed through the shaft hole of the transmission gear, the shaft hole edge of the transmission gear is formed with at least one card slot, and the transmission shaft is formed with an accommodation chamber in the axial direction a receiving plate is disposed in the receiving chamber, and the end of the clamping plate is reciprocally movable in a radial direction of the transmission gear in the receiving chamber to be inserted into or removed from the card slot to realize the transmission shaft and the transmission gear.
  • a translatable transmission device for facilitating steering switching for driving forward and reverse rotation of an output gear comprising: a drive shaft for powering the rotation of the output gear; a positive rotation gear for meshing with the output gear, the drive shaft In combination with the forward rotating gear, the output gear can be driven to rotate forward; the reverse gear set meshes with the output gear, and the drive shaft and the reverse gear set combine to drive the output gear to rotate in the opposite direction; the drive shaft rotates through the forward direction.
  • the shaft hole of the gear is arranged, the edge of the shaft hole of the positive rotation gear is formed with at least one card slot, the drive shaft is formed with a receiving chamber, and the clamping chamber is provided with a card plate, and the end of the card plate can be in the receiving chamber Rotating radially in the forward direction of the gear to insert into the card slot Or remove from the card slot to achieve the combination and separation of the drive shaft and the positive rotation gear.
  • a translatable transmission device for facilitating fast and slow switching for driving fast and slow rotation of the output shaft, comprising: a drive shaft for powering the rotation of the output shaft; at least two sets of transmission gear sets, each set of transmission gear sets Different speeds are used to realize fast and slow rotation of the output shaft; each set of transmission gears includes a driving gear and a driven gear that mesh with each other, the driving gear is sleeved on the driving shaft, and the driven gear is sleeved on the output shaft. And the driving gear and the driving shaft and the driven gear and the output shaft are combined and separated; the driving gear and the driving shaft or the driven gear and the output shaft can be combined and separated, and the shaft passes through the shaft of the gear.
  • the hole is disposed, the shaft hole edge of the gear is formed with at least one card slot, the shaft is formed with a receiving chamber, and the receiving chamber is provided with a clamping plate, and the end of the clamping plate can reciprocate in the radial direction of the gear in the receiving cavity To insert or remove from the card slot to achieve the coupling and separation of the shaft and the gear.
  • the interchangeable transmissive transmission device of the present invention has a structure in which two diameters are too large to be misaligned, and it is difficult to realize a misalignment between the gears, or a structure in which a claw and a hole are easily in contact with each other, and it is difficult to achieve a perforation.
  • the method is converted into the insertion and fastening between the card board and the card slot, which greatly improves the success rate and smoothness of the switching;
  • the translatable transmission device of the present invention is easily engaged by the card plate and the card slot, so that when the "override” phenomenon occurs, the transmission shaft and the transmission gear can be separated, thereby avoiding “beyond” operation. Energy consumption and excessive loss of inertial kinetic energy are still consumed in the state;
  • the translatable transmission device with easy switching of the invention can completely avoid the occurrence of "beyond” operation phenomenon by completely engaging the card plate and the card slot, so that when the "overrun” operation is not required or allowed, the operation phenomenon can be effectively improved. Operational security.
  • FIG. 1 is a schematic structural view of a conventional transmission device for steering switching of a motor vehicle
  • FIG. 2 is a schematic structural view of a conventional transmission device for a fast and slow switching of a motor vehicle
  • Figure 3 is a front elevational view of the first embodiment of the present invention.
  • Figure 4 is a cross-sectional view showing a first embodiment of the present invention.
  • Figure 5 is a plan view of the drive shaft and the accommodating chamber in the first embodiment of the present invention.
  • Figure 6 is a plan view showing the elastic component mounted in the accommodating chamber in the first embodiment of the present invention.
  • Figure 7 is a perspective view of a drum ball in a first embodiment of the present invention.
  • Figure 8 is a perspective view of a card board in a first embodiment of the present invention.
  • Figure 9 is a side view of a first embodiment of the present invention.
  • FIG. 10 is a schematic structural view of the card board in the first embodiment of the present invention when the card board is completely engaged with the card slot;
  • Figure 11 is a structural schematic view showing the position of the card when the sliding assembly and the reverse gear set are engaged in the first embodiment of the present invention
  • Figure 12 is a front elevational view of a second embodiment of the present invention.
  • Figure 13 is a cross-sectional view showing a second embodiment of the present invention.
  • Figure 14 is a plan view of the drive shaft and the accommodating chamber in the second embodiment of the present invention.
  • Figure 15 is a front cross-sectional view showing a drive shaft and a housing chamber in a second embodiment of the present invention.
  • FIG. 16 is a schematic structural view of a card board in a second embodiment of the present invention when it is engaged with a card slot;
  • Figure 17 is a schematic view showing the structure of the end portion of the card corresponding to the combined gear in the second embodiment of the present invention.
  • Figure 18 is a cross-sectional view showing a third embodiment of the present invention.
  • 19 is a schematic structural diagram of an application of the present invention in a fast and slow switching system
  • Figure 20 is a cross-sectional view showing a fourth embodiment of the present invention.
  • Figure 21 is a cross-sectional view of the slide assembly of Figure 20;
  • Figure 22 is a cross-sectional view of the card of Figure 20;
  • Figure 23 is a cross-sectional view showing a fifth embodiment of the present invention.
  • Figure 24 is a cross-sectional view of the slide assembly of Figure 23;
  • Figure 25 is a cross-sectional view showing an embodiment of the card of Figure 23;
  • Figure 26 is a cross-sectional view showing another embodiment of the card of Figure 23;
  • Figure 27 is a cross-sectional view showing a sixth embodiment of the present invention.
  • Figure 28 is a cross-sectional view of the slide assembly of Figure 27;
  • Figure 29 is a cross-sectional view showing an embodiment of the card of Figure 27;
  • Figure 30 is a cross-sectional view of another embodiment of the card of Figure 27.
  • the contents of the present invention will be described below by way of example with reference to FIGS. 3 to 30, respectively, in order to facilitate steering switching and a translatable transmission that facilitates fast and slow switching.
  • the first to third embodiments are translatable transmissions that facilitate steering switching
  • the fourth to sixth embodiments are translatable transmissions that facilitate fast and slow switching.
  • FIGS. 3 to 11 it is a first embodiment of the present invention.
  • the translatable transmission that facilitates steering switching includes an output gear 101 and a drive shaft 102 that powers the rotation of the output gear 101.
  • the one end of the drive shaft 102 adjacent to the output gear 101 is sleeved with a forward rotation gear 103, and the forward rotation gear 103 meshes with the output gear 101.
  • the drive shaft 102 can drive the output gear 101 to rotate forward through the forward rotation gear 103.
  • the position of the forward rotation gear 103 on the drive shaft 102 is provided with a splineless rod section, and the forward rotation gear 103 is on the drive shaft 102. The position is fixed so that the forward rotation gear 103 can be fixedly engaged with the output gear 101.
  • the drive shaft 102 is provided with a card 104, and at least one card slot 105 is formed on the edge of the shaft hole of the forward rotation gear 103.
  • the end of the card 104 on the drive shaft 102 can be moved in the radial direction of the shaft hole of the forward rotation gear 103 so that the end of the card 104 can enter the card slot 105, so that the drive shaft 102 and the drive shaft 102 Fastened to the rotating gear 103, and then passed
  • the forward rotation gear 103 drives the output gear 101 to rotate in the forward direction.
  • the drive shaft 102 is provided with a receiving chamber 106 in which the card 104 is disposed.
  • one end of the card plate 104 is pivotally connected to the side wall of the accommodating chamber 106 (that is, the card board 104 is rotatable about the axis), and the other end is movably disposed in the shaft hole of the forward rotation gear 103, and the card
  • An elastic assembly is provided between the bottom of the plate 104 and the bottom of the receiving chamber 106, and the resilient assembly can provide power to the radial movement of the end of the card 104 in the axial bore of the positive rotating gear 103.
  • the elastic assembly disposed between the card 104 and the bottom of the accommodating chamber 106 includes a spring pin 107 axially disposed in the accommodating chamber 106, and a sleeve.
  • a spring ball 108 on the spring pin 107, a drum ball 109 is disposed between the other end of the spring 108 and the bottom of the card plate 104 near the end of the forward rotation gear 103.
  • the spring pin 107 is a round flat pin shaft, the diameter of the end of the round flat pin shaft is larger than the diameter of the rod portion, and the round flat pin shaft abuts against the end side wall of the accommodating chamber 106 to ensure the linear expansion and contraction of the spring 108. The accuracy of the stroke of the card 104 for radial movement is ensured.
  • the top of the card plate 104 is formed with a stepped gear surface 110, and the height of each of the gear faces 110 gradually becomes higher in a direction away from the forward rotation gear 103.
  • the drive shaft 102 is further sleeved with a movable sliding assembly 111.
  • the inner edge of the shaft hole of the sliding assembly 111 abuts against the blocking surface 110 of the card 104, and can move back and forth between the gear surfaces 110. So that the end of the card plate 104 can move in the radial direction in the shaft hole of the forward rotation gear 103.
  • the sliding assembly 111 and the driving shaft 102 are meshed together by internal and external splines to ensure that the inner edge of the shaft hole of the sliding assembly 111 is accurately aligned with the blocking plate 104.
  • the planes 110 are abutted together.
  • the sliding assembly 111 is coupled to a shifting mechanism (not shown) of the motor vehicle, and the sliding member 111 is moved between the respective shifting faces 110 on the card 104 by operating the shifting mechanism (sliding assembly 111 and the machine)
  • shifting mechanism sliding assembly 111 and the machine
  • the gear surface 110 at the top of the card plate 104 has three non-overrunning forward gear faces, an overrunning forward gear face and a reverse gear face, respectively, wherein the forward rotating gear 103 is adjacent.
  • the gear surface is not beyond the forward gear surface, the gear surface away from the forward rotation gear 103 is the reverse gear surface, the middle is beyond the forward gear surface, and the height of each gear surface 110 is far away.
  • the direction in which the gear 103 is rotated forward is gradually increased.
  • the opening of the card slot 105 faces the drive shaft 102, and is driven.
  • the front portion has a depth greater than the rear depth in the rotational direction of the moving shaft 102, and the bottom wall of the card slot 105 has a sloped shape.
  • the shape of the end portion of the card plate 104 that is movably disposed in the shaft hole of the forward rotation gear 103 is matched with the shape of the card slot 105, and the top surface of the end portion is also beveled, and the shape of the slope and the oblique direction and the card
  • the bottom walls of the grooves 105 are identical.
  • each card slot 105 is uniformly disposed on the edge of the shaft hole of the forward rotating gear 103.
  • a small buffer groove 114 is disposed between the adjacent card slots 105.
  • the shape of the buffer groove 114 is similar to the shape of the card slot 105, and the difference between the two is only in depth. It should be noted that, in this embodiment, the depth of the buffer groove 114 coincides with the depth when the end portion of the card 104 enters the card slot 105, so as to maintain a reasonable structural thickness between the card slot 105 and the buffer groove 114. In turn, the overall strength of the forward rotating gear 103 is ensured.
  • the elastic component can be used and the drive shaft can be driven.
  • the moment of rotation of 102 causes the end of the card 104 to be snapped together with the card slot 105, ensuring complete success of the switching.
  • the translatable transmission that facilitates steering switching also includes a reverse gear set 112 for counter-rotating the output gear 101.
  • the outer circumference of the sliding assembly 111 sleeved on the driving shaft 102 is formed with a coupling tooth 113.
  • One end of the reverse gear set 112 is engaged with the output gear 101, and the other end is engageable with the outer circumference of the sliding assembly 111.
  • the upper coupling teeth 113 mesh or separate from each other.
  • the engaging teeth 113 on the outer circumference of the slide assembly 111 can be engaged with the end portions of the reverse gear set 112, and the drive shaft 102 can be reversed by the slide assembly 111.
  • the gear set 112 rotates such that the output gear 101 rotates in the reverse direction.
  • the shifting mechanism is operated to move the slide assembly 111 toward the forward rotating gear 103, that is, the inner edge of the shaft hole of the slide assembly 111 abuts against the shifting surface of the positive rotating gear 103 on the card 104 (not beyond On the forward gear surface or beyond the forward gear surface).
  • the end of the card 104 can be in the elastic component (the spring pin 107, the spring 108, The drum ball 109) enters the card slot 105 by the action of the drum.
  • the drive shaft 102 and the forward rotation gear 103 are fastened together, and the drive shaft 102 can drive the output gear 101 to rotate in the forward direction by the forward rotation gear 103.
  • the shifting mechanism is operated to move the slide assembly 111 in a direction away from the forward rotating gear 103, that is, a shifting surface of the sliding member 111 that abuts against the positive rotating gear 103 on the card 104. (reverse gear surface).
  • a shifting surface of the sliding member 111 that abuts against the positive rotating gear 103 on the card 104. (reverse gear surface).
  • the drive shaft 102 can drive the output gear 101 to rotate in the reverse direction through the sliding assembly 111 and the reverse gear set 112.
  • the translatable transmission device for facilitating steering switching of the present invention converts two structural modes in which the diameters are too large to be misaligned and slip-in between the gears, and the mechanical structure is inserted and fastened, thereby greatly improving the output gear.
  • the end of the card 104 is completely under the action of the elastic assembly. Entering into the card slot 105 (ie, the lower end of the inclined top surface of the end of the card 104 is at a greater distance from the axis of the drive shaft 102 than the radius of the drive shaft 102), at this time, the drive shaft 102 passes through The output gear 101 is rotated in the forward direction by the turning gear 103.
  • the output gear 101 drives the engine through the forward rotation gear 103 and the drive shaft 102, thereby forcing the vehicle to decelerate and providing auxiliary braking for the vehicle, ensuring that the vehicle is driven under special circumstances (when the slope is as follows). safety.
  • the end portion of the card 104 enters the card slot 105 (ie, the card 104 end)
  • the lower end of the inclined top surface of the portion is at a distance less than or equal to the driving center axis of the drive shaft 102
  • the drive shaft 102 still drives the output gear 101 to rotate in the forward direction by the forward rotation gear 103.
  • the end of the card 104 can be removed from the card slot 105 (due to the shape of the card slot 105, The shape of the end of the card plate 104 and the arrangement of the elastic members are such that the engagement between the drive shaft 102 and the forward rotation gear 103 is released. Furthermore, the output gear 101 will only drive the positive rotating gear 103 to approach zero-load rotation, which greatly reduces the loss of inertial energy of the vehicle when it is "overtaken", and also avoids the engine being over-idled and wasting fuel.
  • the translatable transmission device for facilitating steering switching of the present invention is engaged with the portion of the card slot by the card plate, so that when the "overrun” phenomenon occurs, the drive shaft can be disengaged from the positive rotation gear, and the output gear only drives the positive gear.
  • Rotating gears close to zero-load rotation, avoiding energy consumption and excessive loss of inertia kinetic energy in the “beyond” operating state; and the “fastening” of the card and the card slot makes it unnecessary or impossible to “pass” During operation, it can effectively avoid the occurrence of “overtaking” operation and improve the safety of operation.
  • the difference in this embodiment is that the structure of the card board is different. Only the differences will be described below, and portions similar to those of the first embodiment described above will not be described in detail.
  • the translatable transmission that facilitates steering switching includes an output gear 201, a drive shaft 202 that powers the rotation of the output gear 201, and a reverse gear set 212 that effects reverse rotation of the output gear 201.
  • the forward shaft 203 is disposed on the end of the drive shaft 202 adjacent to the output gear 201.
  • the forward rotation gear 203 is meshed with the output gear 201.
  • the drive shaft 202 can drive the output gear 201 to rotate forward through the forward rotation gear 203.
  • the end of the drive shaft 202 remote from the output gear 201 is sleeved with a coupling gear 215, the combined gear 215 meshes with one end of the reverse gear set 212, and the other end of the reverse gear set 212 meshes with the output gear 201.
  • the output gear 201 can be reversely rotated by driving the reverse gear set 212 in conjunction with the gear 215.
  • the drive shaft 202 is provided with a card 204.
  • At least one slot 205 is formed on the edge of the shaft hole of the forward rotation gear 203, and at least one of the inner edge of the shaft hole of the coupling gear 215 is formed.
  • the card slot 216 is combined.
  • one end of the card plate 204 on the drive shaft 202 is radially movable in the shaft hole of the forward rotation gear 203, so that the end of the card plate 204 enters the card slot 205.
  • the driving shaft 202 is fastened to the forward rotating gear 203, so that the output gear 201 can be rotated in the forward direction; the other end of the clamping plate 204 on the driving shaft 202 can be in the shaft hole of the combined gear 215.
  • the radial movement is performed so that the end of the card 204 can enter the engaging slot 216 of the engaging gear 215, so that the driving shaft 202 and the engaging gear 215 are fastened together, thereby driving the output gear 201 to rotate in the reverse direction.
  • the drive shaft 202 is provided with a receiving chamber 206, and the card 204 is disposed in the receiving chamber 206.
  • the upper portion (shoulder portion) of the card plate 204 is pivotally connected to the side wall of the accommodating chamber 206.
  • One end of the card 204 is movably disposed in the shaft hole of the forward rotation gear 203, and the other end is movably disposed on the coupling gear 215. In the shaft hole.
  • the connection position between the card board 204 on the drive shaft 202 and the side wall of the accommodating chamber 206 is close to the side of the coupling gear 215, and the bottom of the card board 204 and the accommodating chamber
  • An elastic member is disposed between the bottoms of the 206, and the elastic member is disposed on a side close to the forward rotating gear 203.
  • the elastic assembly disposed between the bottom of the card 204 and the bottom of the accommodating chamber 206 includes a radially disposed spring 208 that houses the chamber 206.
  • the bottom portion is formed with a receiving hole.
  • the side wall of the receiving chamber 206 is formed with an arcuate groove along the extending direction of the receiving hole.
  • One end of the spring 208 is disposed in the receiving hole, and the other end of the spring 208 is limited by the curved groove.
  • the position, and the other end of the spring 208 and the bottom of the end of the card 204 are provided with a semi-spherical pin shaft 217 having an end diameter larger than the diameter of the stem.
  • the top of the card plate 204 is formed with a stepped gear surface 210, and the height of each of the gear surface 210 is gradually lowered in a direction away from the forward rotation gear 203.
  • this embodiment There are three gear surface 210 at the top of the middle card plate 204, which are non-overtaking forward gear surface, over-going forward gear surface and reverse gear surface, respectively, wherein the gear surface close to the forward rotation gear 203 is The reverse gear surface, the gear surface close to the combined gear 215 is not beyond the forward gear surface, and the middle is beyond the forward gear surface.
  • the drive shaft 202 is sleeved with a movable sliding assembly 211.
  • the inner edge of the shaft hole of the sliding assembly 211 abuts against the shifting surface 210 of the card 204, and can be along the shifting surface 210.
  • the axial movement of the drive shaft 202 causes the two ends of the card plate 204 to move in the radial direction in the positive rotation gear 203 and the shaft hole of the coupling gear 215, respectively.
  • the coupling of the engaging slot 216 on the inner edge of the shaft hole of the gear 215 is combined.
  • the mouth is facing the driving shaft 202, and the shape of the coupling slot 216 is composed of two parts, the first part is rectangular (ie, the opening section), the second part is V-shaped (ie, the bottom wall), and the card board 204 corresponds to the combining card slot 216.
  • the shape of the end portion matches the shape of the combined card slot 216.
  • a plurality of engaging slots 216 are disposed on the inner edge of the shaft hole of the gear 215, and the adjacent engaging slots 216 are closely connected, so that even the tip between the adjacent engaging slots 216 and the end of the card 204 are present.
  • the shape and function of the card slot 205 in this embodiment are similar to those in the first embodiment, and will not be described in detail.
  • the shifting mechanism is operated to move the sliding assembly 211 toward the engaging gear 215, that is, the inner side of the shaft hole of the sliding assembly 211 abuts against the shifting surface of the engaging gear 215 on the top surface of the card 204 (non-passing forward direction) The gear surface or beyond the forward gear surface).
  • one end of the card 204 can enter the card slot 205 on the forward rotation gear 203, and the other end of the card 204 is separated from the coupling slot 216 on the coupling gear 215.
  • the drive shaft 202 and the forward rotation gear 203 are fastened together, and the drive shaft 202 can drive the output gear 201 to rotate forward by the forward rotation gear 203.
  • the shifting mechanism is operated to move the slide assembly 211 in the direction of the forward rotation gear 203, that is, to cause the inner side of the shaft hole of the slide assembly 211 to abut against the gear of the forward rotation gear 203 on the top surface of the card 204.
  • the end of the card 204 can enter the coupling slot 216 of the coupling gear 215, and the other end of the card 204 is separated from the slot 205 of the forward rotation gear 203.
  • the drive shaft 202 and the coupling gear 215 are fastened together, and the drive shaft 202 can drive the output gear 201 to rotate in the reverse direction by combining the gear 215 and the reverse gear set 212.
  • the 205 is removed so that the drive shaft 202 and the forward rotation gear 203 are always in the engaged state. Further, the output gear 201 drives the engine through the forward rotation gear 203 and the drive shaft 202, thereby forcing the vehicle to decelerate and providing auxiliary braking for the vehicle, ensuring that the vehicle is driven under special circumstances (when the slope is as follows). safety.
  • the output gear 201 will only drive the positive rotation gear 203 to approach zero-load rotation, which greatly reduces the loss of inertial energy of the motor vehicle during "overtaking” coasting, and also avoids the engine being over-idled and wasting fuel.
  • FIG. 18 it is a third embodiment of the present invention.
  • the main difference in this embodiment is that the card 304 is freely disposed in the accommodating chamber 306 as compared with the first embodiment described above. Only the differences will be described below, and portions similar to those of the first embodiment described above will not be described in detail.
  • the card plate 304 and the accommodating chamber 306 are freely disposed, that is, the card plate 304 and the accommodating chamber 306 are not connected to each other.
  • One end of the card plate 304 is movably disposed in the shaft hole of the forward rotation gear 303.
  • the bottom of the card plate 304 is formed with a guide cylinder.
  • the bottom surface of the accommodation chamber 306 is formed with a receiving hole for guiding the cylinder and the bottom surface of the accommodating chamber 306.
  • the radial direction of the drive shaft 304 is provided with a resilient assembly (ie, a spring 308), wherein the spring 308 is at least two and disposed separately, one end of the spring 308 is hooped on the guide cylinder and the other end is inserted into the receiving hole.
  • the translatable transmission for facilitating fast and slow switching is used to drive the output shaft to rotate rapidly and slowly, including the output shaft 401, the drive shaft 402, and the transmission gear set.
  • the drive shaft 402 provides power for the rotation of the output shaft 401;
  • the transmission gear set is at least two sets, and each set of transmission gear sets transmits different rotational speeds for realizing rapid and slow rotation of the output shaft 401; each set of transmission gears
  • the group includes an intermeshing driving gear and a driven gear.
  • the driving gear is sleeved on the driving shaft 402, the driven gear is sleeved on the output shaft 401, and the driving gear and the driving shaft 402 and the driven gear and the output shaft 401
  • the present embodiment includes five sets of transmission gear sets that are sequentially disposed.
  • the driven gear 412 and the output shaft 401 are combined and disengageable; in the second set of transmission gear sets, the driving gear 421 and the drive shaft 402 are combined and separable;
  • the driven gear 432 and the output shaft 401 are combined and disengageable; in the fourth set of transmission gear sets, the driving gear 441 and the driving shaft 402 are combined and disengageable; in the fifth set of transmission gear sets,
  • the driven gear 452 and the output shaft 401 are detachable and separable.
  • first set of transmission gear sets in this embodiment may correspond to one gear
  • the second set of transmission gear sets may correspond to three gears
  • the third set of transmission gear sets may correspond to four gears
  • the fourth set of transmissions The gear set can correspond to the fifth gear
  • the fifth set of gear gears can correspond to the second gear.
  • the shaft is disposed through the shaft hole of the gear, the shaft hole edge of the gear is formed with at least one card slot, the shaft is formed with a receiving chamber, and the receiving chamber is provided with a card plate The end of the card plate can reciprocate in the radial direction of the gear in the accommodating chamber to be inserted into or removed from the card slot to realize the coupling and separation of the shaft and the gear.
  • the card plate is disposed in the axial direction of the shaft in the accommodating chamber, and the accommodating chamber is provided with an elastic component, and the elastic component abuts against the bottom of the end portion of the card plate, and can push the end of the card plate to move along the radial direction of the gear
  • the top of the card plate is formed with a stepped gear surface, and the sliding sleeve is sleeved on the shaft, and the inner edge of the shaft hole of the sliding assembly abuts against the gear surface at the top of the card plate and can be on the stepped gear surface
  • the reciprocating movement causes the end of the card to reciprocate in the radial direction of the gear.
  • one end of the card plate is pivotally connected to the side wall of the accommodating chamber, and the other end is movably disposed in the shaft hole of the transmission gear, and the elastic assembly is along the transmission shaft in the accommodating chamber.
  • the axial arrangement, the end of the elastic component abuts against the bottom of the end of the card plate that is disposed in the shaft hole of the transmission gear, and can push the end of the card plate to move along the radial direction of the transmission gear to be inserted into the card In the slot.
  • the elastic component includes a spring, the spring is disposed in the axial direction of the transmission shaft in the accommodating chamber, and the end of the spring is provided with a drum-shaped ball, and the spring is disposed on the shaft hole of the transmission gear through the drum-shaped ball and the card plate The bottom of the middle end abuts.
  • the driving gear 431 in the third set of transmission gear sets can be used as the sliding assembly in the second set of transmission gear sets and the fourth set of transmission gear sets;
  • the driven gears 422 in the second set of transmission gear sets It can be used as a sliding assembly in the first set of transmission gear sets and the third set of transmission gear sets;
  • the driven gear 442 in the fourth set of transmission gear sets can be used as a sliding assembly in the fifth set of transmission gear sets.
  • the separated state of the first set of transmission gear sets the inner edge of the shaft hole of the driven gear 422 in the second set of transmission gear sets abuts against the separation gear surface of the card plate 413 in the first set of transmission gear sets, the card board The 413 is separated from the driven gear 412 of the first set of transmission gear sets, that is, the first set of transmission gear sets are in a separated state.
  • the overrunning state of the first set of transmission gear sets driving the driven gear 422 of the second set of transmission gear sets toward the driven gear 412 of the first set of transmission gear sets by the plucking plate 403, and causing the driven gear 422
  • the inner edge of the shaft hole abuts against the overcoming engagement surface of the card plate 413, the card plate 413 rotates upward under the force of the spring, and the card plate 413 is combined with the driven gear 412, that is, the first set of transmission gear sets are beyond Combined state.
  • the non-overrunning state of the first set of transmission gear sets the driven gear 422 of the second set of transmission gear sets is driven to move toward the driven gear 412 of the first set of transmission gear sets by the plucking plate 403, and is driven
  • the inner edge of the shaft hole of the gear 422 abuts against the non-overtaking combined gear surface of the card plate 413, the card plate 413 rotates upward under the force of the spring, and the card plate 413 and the driven gear 412 are completely combined, that is, the first set of transmission gears
  • the group is in a non-transcendental state.
  • the separated state of the second set of transmission gear sets the inner side of the shaft hole of the driving gear 431 in the third set of transmission gear sets abuts against the separation gear surface of the card plate 423 in the second set of transmission gear sets, the card plate 423 Separated from the driving gear 421 in the second set of transmission gear sets, that is, the second set of transmission gear sets are in a separated state.
  • the overrunning state of the second set of transmission gear sets driving the driving gear 431 of the third set of transmission gear sets to move toward the driving gears 421 of the second set of transmission gear sets by the drawing plate 404, and driving the shaft holes of the driving gears 431
  • the inner edge abuts against the over-combining gear surface of the card plate 423, the card plate 423 rotates upward under the spring force, and the card plate 423 is combined with the driving gear 421, that is, the second set of transmission gear sets are in the over-combined state.
  • the non-overrunning state of the second set of transmission gear sets the driving gear 431 in the third set of transmission gear sets is continuously driven to move toward the driving gear 421 in the second set of transmission gear sets by the plucking plate 404, and the driving gear 431 is driven from the driving gear 431
  • the inner edge of the shaft hole abuts against the non-overtaking combined gear surface of the card plate 423, the card plate 423 rotates upward under the force of the spring, and the card plate 423 is completely combined with the driving gear 421, that is, the second set of transmission gear sets are not Beyond the state of integration.
  • the separated state of the third set of transmission gear sets the inner edge of the shaft hole of the driven gear 422 in the second set of transmission gear sets abuts against the separation gear surface of the card plate 433 in the third set of transmission gear sets, the card board The 433 is separated from the driven gear 432 of the third set of transmission gear sets, that is, the third set of transmission gear sets are in a separated state.
  • the overrunning state of the third set of transmission gear sets driving the driven gear 422 of the second set of transmission gear sets toward the driven gear 432 of the third set of transmission gear sets by the plucking plate 403, and driving the driven gear 422
  • the inner edge of the shaft hole abuts against the overtaking engagement surface of the card plate 433, the card plate 433 rotates upward under the force of the spring, and the card plate 433 is combined with the driven gear 432, that is, the third set of transmission gear sets are beyond Combined state.
  • the non-overrunning state of the third set of transmission gear sets the driven gear 422 of the second set of transmission gear sets is driven to move toward the driven gear 432 of the third set of transmission gear sets by the plucking plate 403, and is driven
  • the inner edge of the shaft hole of the gear 422 abuts against the non-overtaking combined gear surface of the card plate 433, the card plate 433 rotates upward under the force of the spring, and the card plate 433 and the driven gear 432 are completely combined, that is, the first set of transmission gears
  • the group is in a non-transcendental state.
  • the overrunning state of the fourth set of transmission gear sets driving the driving gear 431 of the third set of transmission gear sets to move toward the driving gears 441 of the fourth set of transmission gear sets by the drawing plate 404, and driving the shaft holes of the driving gears 431
  • the inner edge abuts against the over-combined gear surface of the card plate 443, the card plate 443 rotates upward under the spring force, and the card plate 443 is combined with the driving gear 441, that is, the fourth set of transmission gear sets are in the over-combined state.
  • the non-overrunning state of the fourth set of transmission gear sets the driving gear 431 in the third set of transmission gear sets is continuously driven to move toward the driving gear 441 in the fourth set of transmission gear sets by the plucking plate 404, and the driving gear 431 is driven from the driving gear 431
  • the inner edge of the shaft hole abuts against the non-overtaking combined gear surface of the card plate 443, the card plate 443 rotates upward under the force of the spring, and the card plate 443 is completely combined with the driving gear 441, that is, the fourth set of transmission gear sets are not Beyond the state of integration.
  • the separation state of the fifth set of transmission gear sets the inner side of the shaft hole of the driven gear 442 in the fourth set of transmission gear sets abuts against the separation gear surface of the card plate 453 in the fifth set of transmission gear sets, the card board The 453 is separated from the driven gear 452 in the fifth set of transmission gear sets, that is, the fifth set of transmission gear sets are in a separated state.
  • the overrunning state of the fifth set of transmission gear sets the driven gear 442 of the fourth set of transmission gear sets is driven by the plucking plate 405 toward the driven gear 452 of the fifth set of transmission gear sets, and the driven gear 442 is driven
  • the inner edge of the shaft hole abuts against the over-combined gear surface of the card plate 453, the card plate 453 rotates upward under the force of the spring, and the card plate 453 is combined with the driven gear 452, that is, the fifth set of transmission gear sets are beyond Combined state.
  • the non-overrunning state of the fifth set of transmission gear sets the driven gear 442 of the fourth set of transmission gear sets is driven to move toward the driven gear 452 of the fifth set of transmission gear sets by the plucking plate 405, and is driven
  • the inner edge of the shaft hole of the gear 442 abuts against the non-overtaking combined gear surface of the card plate 453, the card plate 453 rotates upward under the force of the spring, and the card plate 453 is completely combined with the driven gear 452, that is, the fifth set of transmission gears.
  • the group is in a non-transcendental state.
  • the structure in this embodiment corresponds to the forward rotating gear end in the second embodiment described above, and the principle corresponds to the above-described fourth embodiment (the only difference is that the moving direction of the fork plate is opposite), and details are not described herein again.
  • the structure in this embodiment corresponds to the forward rotating gear end of the above-described third embodiment (the only difference is that the moving direction of the fork plate in this embodiment is opposite to the moving direction of the sliding assembly in the third embodiment),
  • the principle corresponds to the fifth embodiment described above, and details are not described herein again.
  • the translatable transmission device of the present invention has a structure in which two diameters are too large to be misaligned, and it is difficult to realize a misalignment between the gears, or a structure in which the claws and the holes are likely to be in contact with each other, and it is difficult to realize the coupling of the perforations. It has become the plugging and fastening between the card board and the card slot, which greatly improves the success rate and smoothness of the switching.
  • the translatable transmission device of the present invention can be engaged with the portion of the card slot by the card plate, so that the "transcend” phenomenon can be disengaged from the transmission gear to avoid the "overrun” operation.
  • energy is still consumed, and excessive loss of inertial kinetic energy; at the same time, the easily translatable transmission of the present invention is fully engaged by the card and the card slot, so that when the "overrun” operation is not required or allowed It can effectively avoid the occurrence of "beyond” operation phenomenon and improve the safety of operation.
  • the above is a transmission device on a motor vehicle as an example, and the translatable transmission device of the present invention which is easy to switch is described in detail. It should be noted, however, that the interchangeable transmission of the present invention can be applied to any field having a transmission, such as a ship, an aircraft, etc., as needed, and is not necessarily limited to the automotive field described below.

Abstract

一种便于切换的可超越式传动装置，该传动装置包括传动齿轮和穿过传动齿轮轴孔设置的传动轴（102），传动齿轮的轴孔边缘形成有至少一个卡槽（105），传动轴（102）的轴向上形成有容纳腔室，容纳腔室中设置有卡板（104），卡板（104）的端部可在容纳腔室中沿传动齿轮的径向往复移动，以插入到卡槽（105）中或从卡槽（105）中移出，实现传动轴（102）与传动齿轮的结合与分离，便于切换的可超越式传动装置能够使传动过程中的切换顺利，能够有效节省能源。

Description

便于切换的可超越式传动装置 技术领域
本发明涉及一种传动装置，尤其涉及一种便于切换的可超越式传动装置。
背景技术
传动装置是把动力装置的动力传递给工作机构等的中间设备。其中，以机动车为例，传动装置的基本功用是将发动机发出的动力传递给机动车的驱动车轮，以产生驱动力，使机动车能在一定速度上行驶。
如图1所示，现有的机动车中用于转向切换的传动装置包括输出齿轮1、主动齿轮2和反向齿轮组3。其中，输出齿轮1与差速器(图中未示)相连，可以正向转动和反向转动，以实现机动车的向前、向后行驶。
主动齿轮2与驱动轴4相连，驱动轴4与发动机输出轴(图中未示)相连，主动齿轮2可以在驱动轴4的带动下转动，以便为输出齿轮1的转动提供原始动力。此外，主动齿轮2还可通过拨叉板5与换挡装置中的拨叉杆6相连，在拨叉杆6的带动下，主动齿轮2可以在驱动轴4上轴向移动，以分别与输出齿轮1和反向齿轮组3相啮合，从而实现输出齿轮1的正向转动和反向转动，也即机动车的向前、向后行驶。
反向齿轮组3的一端靠近输出齿轮1设置，并与输出齿轮1一直保持啮合状态，另一端则远离输出齿轮1设置，并处于能够与主动齿轮2相啮合的位置，反向齿轮组能够使输出齿轮1实现反向转动。
当需要使机动车处于前进状态时，操控变挡装置(图中未示)，使变挡装置中的拨叉杆6通过拨叉板5带动主动齿轮2朝向靠近输出齿轮1的方向移动，并促使主动齿轮2与输出齿轮1相啮合。由此，输出齿轮1即可在主动齿轮2的带动下正向转动，使机动车处于前进状态。
当需要使机动车处于后退状态时，操控变挡装置(图中未示)，使变挡装置中的拨叉杆6通过拨叉板5带动主动齿轮2朝向远离输出齿轮1的方向 移动，并促使主动齿轮2与反向齿轮组3的一端相啮合。由此，便可通过主动齿轮2、反向齿轮组3带动输出齿轮1反向转动，从而使机动车处于后退状态。
如图2所示，现有的机动车中用于快慢切换的传动装置包括驱动轴21、输出轴25和两套传动齿轮组(快速传动齿轮组和慢速传动齿轮组)。其中，快速传动齿轮组包括套设在驱动轴21上的快速主动齿轮24和套设在输出轴25上的快速从动齿轮27，快速主动齿轮24和快速从动齿轮27相互啮合；慢速传动齿轮组包括套设在驱动轴21上的慢速主动齿轮22和套设在输出轴25上的慢速从动齿轮26，慢速主动齿轮22和慢速从动齿轮26相互啮合。
驱动轴21上在慢速主动齿轮22和快速主动齿轮24之间还设置有拨轮23。其中，慢速主动齿轮22和快速主动齿轮24上分别形成有结合孔，拨轮23上形成有结合爪。此外，拨轮23还可通过拨叉板(图中未示)与换挡装置中的拨叉杆(图中未示)相连，在拨叉杆的带动下，拨轮23可以在驱动轴21上轴向移动，以分别与慢速主动齿轮22和快速主动齿轮24相结合，从而实现输出轴25的慢速转动和快速转动，也即机动车的慢速、快速行驶。
当需要使机动车处于慢速行驶状态时，操控变挡装置(图中未示)，使变挡装置中的拨叉杆通过拨叉板带动拨轮23朝向靠近慢速主动齿轮22的方向移动，并促使拨轮23上的结合爪与慢速主动齿轮22上的结合孔相结合。由此，输出轴25即可在驱动轴21、慢速主动齿轮22和慢速从动齿轮26的带动下转动，使机动车处于慢速行驶状态。
当需要使机动车处于快速行驶状态时，操控变挡装置(图中未示)，使变挡装置中的拨叉杆通过拨叉板带动拨轮23朝向靠近快速主动齿轮24的方向移动，并促使拨轮23上的结合爪与快速主动齿轮24上的结合孔相结合。由此，输出轴25即可在驱动轴21、快速主动齿轮24和快速从动齿轮27的带动下转动，使机动车处于快速行驶状态。
上述现有的机动车用于转向切换和快慢切换的传动装置主要存在以下问题：
1)机动车用于转向切换的传动装置中，由于机动车在前进、后退的切换过程中需要主动齿轮2靠近输出齿轮1并与其相啮合，或者需要主动齿轮 2靠近反向齿轮组3的一端并与其相啮合才能实现机动车向前、向后行驶的切换，而这种齿轮间的错位滑入啮合常常会因为两个齿轮的直径相差过大而出现严重的交叉碰撞和阻滞，从而导致齿轮间无法正常滑入啮合，这样也就会使得切换失败，甚至还有可能导致齿轮损坏；
2)机动车用于转向切换的传动装置中，在机动车行驶过程中，当输出齿轮1的相对转速高于驱动轴4的转速，也即出现“超越”现象时，输出齿轮1反而会带动驱动轴4转动，进而也就会携带发动机负荷运转，由此便使得机动车可“超越”滑行距离变短，以及油耗增加；
3)机动车用于快慢切换的传动装置中，也存在与上述情况类似的问题，即结合爪与结合孔接触时的抵触问题、以及超越行驶问题。
发明内容
本发明的目的在于提供一种切换顺利且能有效节省能源的便于切换的可超越式传动装置。
为实现上述目的，本发明的一种便于切换的可超越式传动装置的具体技术方案为：
一种便于切换的可超越式传动装置，包括传动齿轮和穿过传动齿轮轴孔设置的传动轴，传动齿轮的轴孔边缘形成有至少一个卡槽，传动轴的轴向上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿传动齿轮的径向往复移动，以插入到卡槽中或从卡槽中移出，实现传动轴与传动齿轮的结合与分离。
一种便于转向切换的可超越式传动装置，用于驱动输出齿轮正向和反向转动，包括：驱动轴，为输出齿轮的转动提供动力；正向转动齿轮，与输出齿轮相啮合，驱动轴与正向转动齿轮相结合可驱动输出齿轮正向转动；反向齿轮组，与输出齿轮相啮合，驱动轴与反向齿轮组相结合可驱动输出齿轮反向转动；驱动轴穿过正向转动齿轮的轴孔设置，正向转动齿轮的轴孔边缘形成有至少一个卡槽，驱动轴上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿正向转动齿轮的径向往复移动，以插入到卡槽中 或从卡槽中移出，实现驱动轴与正向转动齿轮的结合与分离。
一种便于快慢切换的可超越式传动装置，用于驱动输出轴快速和慢速转动，包括：驱动轴，为输出轴的转动提供动力；至少两套传动齿轮组，各套传动齿轮组传递的转速不同，用于实现输出轴的快速和慢速转动；每套传动齿轮组中都包括相互啮合的主动齿轮和从动齿轮，主动齿轮套设在驱动轴上，从动齿轮套设在输出轴上，且主动齿轮与驱动轴和从动齿轮与输出轴中有一组为可结合与分离的；可结合与分离的主动齿轮与驱动轴或从动齿轮与输出轴中，轴穿过齿轮的轴孔设置，齿轮的轴孔边缘形成有至少一个卡槽，轴上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿齿轮的径向往复移动，以插入到卡槽中或从卡槽中移出，实现轴与齿轮的结合与分离。
与现有的传动装置相比，本发明的便于切换的可超越式传动装置的优点在于：
1)本发明的便于切换的可超越式传动装置将两个直径相差过大而难于实现齿轮间错位滑入啮合的结构方式或爪与孔之间易发生抵触情况而难以实现齿孔结合的结构方式转换成了卡板与卡槽之间的插合、扣接，大大提高了切换的成功率和顺畅度；
2)本发明的便于切换的可超越式传动装置通过卡板与卡槽的部分扣合，使得在出现“超越”现象时，可使传动轴与传动齿轮脱离开来，避免了“超越”运行状态下仍会消耗能源，以及惯性动能的过度损失；
3)本发明的便于切换的可超越式传动装置通过卡板与卡槽的完全扣合，使得在不需要或不允许“超越”运转时，可有效避免“超越”运转现象的发生，提高了运行的安全性。
附图概述
图1为现有的机动车用于转向切换的传动装置的结构示意图；
图2为现有的机动车用于快慢切换的传动装置的结构示意图；
图3为本发明的第一实施例的主视图；
图4为本发明的第一实施例的剖视图；
图5为本发明的第一实施例中的驱动轴及容纳腔室的俯视图；
图6为本发明的第一实施例中的容纳腔室内安装弹性组件后的俯视图；
图7为本发明的第一实施例中的鼓形滚珠的立体图；
图8为本发明的第一实施例中的卡板的立体图；
图9为本发明的第一实施例的侧视图；
图10为本发明的第一实施例中的卡板与卡槽完全扣合时的结构示意图；
图11为本发明的第一实施例中的滑动组件与反向齿轮组啮合时卡板所处位置的结构示意图；
图12为本发明的第二实施例的主视图；
图13为本发明的第二实施例的剖视图；
图14为本发明的第二实施例中的驱动轴及容纳腔室的俯视图；
图15为本发明的第二实施例中的驱动轴及容纳腔室的正向剖视图；
图16为本发明的第二实施例中的卡板与结合卡槽扣合时的结构示意图；
图17为本发明的第二实施例中的卡板上与结合齿轮相对应的端部的结构示意图；
图18为本发明的第三实施例的剖视图；
图19为本发明应用在快慢切换系统中的结构示意图；
图20为本发明的第四实施例的剖视图；
图21为图20中的滑动组件的剖视图；
图22为图20中的卡板的剖视图；
图23为本发明的第五实施例的剖视图；
图24为图23中的滑动组件的剖视图；
图25为图23中的卡板的一实施例的剖视图；
图26为图23中的卡板的另一实施例的剖视图；
图27为本发明的第六实施例的剖视图；
图28为图27中的滑动组件的剖视图；
图29为图27中的卡板的一实施例的剖视图；
图30为图27中的卡板的另一实施例的剖视图。
本发明的较佳实施方式
为了更好的了解本发明的目的、结构及功能，下面结合附图，对本发明的一种便于切换的可超越式传动装置做进一步详细的描述。
下面结合图3至图30，分别以便于转向切换和便于快慢切换的可超越式传动装置为例来对本发明的内容进行说明。其中，第一实施例至第三实施例为便于转向切换的可超越式传动装置，第四实施例至第六实施例为便于快慢切换的可超越式传动装置。
如图3至图11所示，其为本发明的第一实施例。
如图3所示，本实施例中，便于转向切换的可超越式传动装置包括输出齿轮101和为输出齿轮101的转动提供动力的驱动轴102。其中，驱动轴102上靠近输出齿轮101的一端套设有正向转动齿轮103，正向转动齿轮103与输出齿轮101相啮合，驱动轴102可通过正向转动齿轮103带动输出齿轮101正向转动。应注意的是，如图11所示，本实施例中，驱动轴102上套设正向转动齿轮103的位置处设有无花键的光杆段，且正向转动齿轮103在驱动轴102上的位置是固定不变的，以便正向转动齿轮103可与输出齿轮101固定啮合在一起。
如图4和图10所示，驱动轴102上设置有卡板104，正向转动齿轮103的轴孔边缘上形成有至少一个卡槽105。其中，驱动轴102上的卡板104的端部可在正向转动齿轮103的轴孔中沿径向移动，以便卡板104的端部可进入到卡槽105中，使得驱动轴102与正向转动齿轮103扣合在一起，进而通 过正向转动齿轮103带动输出齿轮101正向转动。
如图4所示，驱动轴102上开设有容纳腔室106，卡板104设置在容纳腔室106中。其中，卡板104的一端枢轴连接在容纳腔室106的侧壁上(也即，卡板104可绕该轴转动)，另一端活动设置在正向转动齿轮103的轴孔中，且卡板104的底部与容纳腔室106的底部之间设置有弹性组件，弹性组件可为卡板104的端部在正向转动齿轮103的轴孔中的径向移动提供动力。
如图4至图7所示，本实施例中，设置在卡板104与容纳腔室106的底部之间的弹性组件包括轴向设置在容纳腔室106中的弹簧销轴107，以及套设在弹簧销轴107上的弹簧108，弹簧108的另一端与卡板104上靠近正向转动齿轮103的端部的底部之间设置有鼓形滚珠109。其中，弹簧销轴107为圆平头销轴，圆平头销轴的端部直径大于杆部直径，圆平头销轴抵靠在容纳腔室106的端侧壁上，以保证弹簧108作直线伸缩，确保卡板104作径向移动的行程的准确性。
如图4和图8所示，卡板104的顶部形成有阶梯状的挡位面110，且各挡位面110的高度沿远离正向转动齿轮103的方向逐渐变高。此外，驱动轴102上还套设有可移动的滑动组件111，滑动组件111的轴孔内沿抵靠在卡板104的挡位面110上，并能够在各挡位面110之间来回移动，以使卡板104的端部可在正向转动齿轮103的轴孔中沿径向移动。应注意的是，本实施例中，滑动组件111与驱动轴102之间是通过内、外花键啮合在一起的，以保证滑动组件111的轴孔内沿准确地与卡板104上的挡位面110抵靠在一起。此外，滑动组件111与机动车的变档机构(图中未示)相连，通过操作变档机构可使滑动组件111在卡板104上的各挡位面110之间移动(滑动组件111与机动车的变档机构的具体连接方式可参考现有技术)。
如图8所示，卡板104顶部的挡位面110具有三个，分别为非超越正向挡位面、超越正向挡位面和反向挡位面，其中，靠近正向转动齿轮103的挡位面为非超越正向挡位面，远离正向转动齿轮103的挡位面为反向挡位面，中间的为超越正向挡位面，且各挡位面110的高度沿远离正向转动齿轮103的方向逐渐变高。
如图10所示，本实施例中，卡槽105的开口朝向驱动轴102，且在驱 动轴102的转动方向上前部深度大于后部深度，卡槽105的底壁呈斜面状。卡板104上活动设置在正向转动齿轮103的轴孔中的端部的形状与卡槽105的形状相配合，该端部的顶面也呈斜面状，且斜面的形状和斜向与卡槽105的底壁相一致。
如图9和图10所示，为了保证机动车切换到向前行驶时的平稳性和柔和性，本实施例中，正向转动齿轮103的轴孔边缘上均匀设置有四个卡槽105，且相邻的卡槽105之间设置有小型的缓冲槽114，其中，缓冲槽114的形状与卡槽105的形状近似设置，两者仅是在深度上存在区别。应注意的是，本实施例中，缓冲槽114的深度与卡板104的端部部分进入到卡槽105中时的深度一致，以便使卡槽105与缓冲槽114之间保持合理的结构厚度，进而保证了正向转动齿轮103的整体强度。
通过上述结构的设置，使得输出齿轮101切换到正向转动时，即使发生了卡板104的端部与卡槽105两侧突起处相抵的情况，也可在弹性组件的作用下并在驱动轴102转动的瞬间使卡板104的端部与卡槽105扣合在一起，保证了切换的完全成功。
如图3和图11所示，便于转向切换的可超越式传动装置还包括用于使输出齿轮101反向转动的反向齿轮组112。此外，本实施例中，驱动轴102上套设的滑动组件111的外圆周上形成有结合齿113，反向齿轮组112的一端与输出齿轮101相啮合，另一端可与滑动组件111外圆周上的结合齿113相互啮合或分离。由此，当需要使输出齿轮101反向转动时，可使滑动组件111外圆周上的结合齿113与反向齿轮组112的端部相啮合，驱动轴102便可通过滑动组件111带动反向齿轮组112转动从而使得输出齿轮101反向转动。
下面结合附图对本实施例的便于转向切换的可超越式传动装置中的“转向切换”操作进行描述：
当需要使输出齿轮101正向转动时。操作变档机构，使滑动组件111朝向正向转动齿轮103移动，也即，使滑动组件111的轴孔内沿抵靠在卡板104上的靠近正向转动齿轮103的挡位面(非超越正向挡位面或超越正向挡位面)上。此时，卡板104的端部便可在弹性组件(弹簧销轴107、弹簧108、 鼓形滚珠109)的作用下进入到卡槽105中。由此，驱动轴102与正向转动齿轮103便扣合在一起，进而驱动轴102便可通过正向转动齿轮103带动输出齿轮101正向转动。
当需要使输出齿轮101反向转动时。操作变档机构，使滑动组件111朝向远离正向转动齿轮103的方向移动，也即，使滑动组件111的轴孔内沿抵靠在卡板104上的远离正向转动齿轮103的挡位面(反向挡位面)上。此时，在滑动组件111的轴孔内沿的压力下，卡板104的端部便会从卡槽105中移出，而滑动组件111上的结合齿113便可与反向齿轮组112的一端相啮合。由此，驱动轴102即可通过滑动组件111、反向齿轮组112来带动输出齿轮101反向转动。
本发明的便于转向切换的可超越式传动装置将两个直径相差过大而难于实现齿轮间错位滑入啮合的结构方式转换成了机械结构之间的插合、扣接，大大提高了输出齿轮正转和反转切换的成功率和顺畅度。
下面结合附图对本实施例的便于转向切换的可超越式传动装置中的“非超越”和“可超越”操作进行描述：
当滑动组件111的轴孔内沿位于卡板104上最靠近正向转动齿轮103的挡位面(非超越正向挡位面)上时，卡板104的端部在弹性组件的作用下完全进入到卡槽105中(也即，卡板104端部的斜面状顶面上的较低一端与驱动轴102轴中心线的距离大于驱动轴102的半径)，此时，驱动轴102通过正向转动齿轮103带动输出齿轮101正向转动。如果在行驶过程中出现输出齿轮101的相对转速高于驱动轴102的转速，也即发生“超越”现象时，由于卡板104的端部完全进入到卡槽105中，便无法从卡槽105中移出，使得驱动轴102与正向转动齿轮103之间一直保持扣合状态。进而，输出齿轮101便会通过正向转动齿轮103和驱动轴102驱动发动机运转，进而迫使机动车减速并为机动车提供辅助制动，保证了在特殊情况下(如下坡时)机动车行驶的安全性。
当滑动组件111的轴孔内沿位于卡板104上中间的挡位面上(超越结合挡位面)时，卡板104的端部部分进入到卡槽105中(也即，卡板104端部的斜面状顶面上的较低一端与驱动轴102轴中心线的距离小于或等于驱动 轴102的半径)，此时，驱动轴102仍是通过正向转动齿轮103带动输出齿轮101正向转动。如果在行驶过程中发生“超越”现象时，由于卡板104的端部只是部分进入到卡槽105中，卡板104的端部便可从卡槽105中移出(由于卡槽105的形状、卡板104端部的形状、以及弹性组件的设置)，使得驱动轴102与正向转动齿轮103之间的扣合解除。进而，输出齿轮101便会仅带动正向转动齿轮103接近零负荷转动，大大降低了机动车在“超越”滑行时惯性能量的损耗，同时也避免了发动机出现超怠速状况而浪费燃油。
本发明的便于转向切换的可超越式传动装置通过卡板与卡槽的部分扣合，使得在出现“超越”现象时，可使驱动轴与正向转动齿轮脱离开来，输出齿轮仅带动正向转动齿轮接近零负荷转动，避免了“超越”运行状态下仍会消耗能源，以及惯性动能的过度损失；而通过卡板与卡槽的完全扣合，使得在不需要或不允许“超越”运转时，可有效避免“超越”运转现象的发生，提高了运行的安全性。
如图12至图17所示，其为本发明的第二实施例。
与上述第一实施例相比，本实施例的区别在于：卡板的结构不同。下面仅就该区别点进行说明，与上述第一实施例相似的部分不再详述。
如图12所示，便于转向切换的可超越式传动装置包括输出齿轮201、为输出齿轮201的转动提供动力的驱动轴202、以及实现输出齿轮201反向转动的反向齿轮组212。
其中，驱动轴202上靠近输出齿轮201的一端套设有正向转动齿轮203，正向转动齿轮203与输出齿轮201相啮合，驱动轴202可通过正向转动齿轮203带动输出齿轮201正向转动；驱动轴202上远离输出齿轮201的一端套设有结合齿轮215，结合齿轮215与反向齿轮组212的一端相啮合，反向齿轮组212的另一端与输出齿轮201相啮合，驱动轴202可通过结合齿轮215带动反向齿轮组212转动而使得输出齿轮201反向转动。
如图13和图16所示，驱动轴202上设置有卡板204，正向转动齿轮203的轴孔边缘上形成有至少一个卡槽205，结合齿轮215的轴孔内沿上形成有至少一个结合卡槽216。其中，驱动轴202上的卡板204的一个端部可在正向转动齿轮203的轴孔中沿径向移动，以便卡板204的端部进入到卡槽205 中，使得驱动轴202与正向转动齿轮203扣合在一起，进而便可带动输出齿轮201正向转动；驱动轴202上的卡板204的另一个端部可在结合齿轮215的轴孔中沿径向移动，以便卡板204的端部可进入到结合齿轮215的结合卡槽216中，使得驱动轴202与结合齿轮215扣合在一起，进而便可带动输出齿轮201反向转动。
如图13至图15所示，驱动轴202上开设有容纳腔室206，卡板204设置在容纳腔室206中。其中，卡板204的上部(肩窝部)枢轴连接在容纳腔室206的侧壁上，卡板204的一端活动设置在正向转动齿轮203的轴孔中，另一端活动设置在结合齿轮215的轴孔中。
如图13所示，本实施例中，驱动轴202上的卡板204与容纳腔室206的侧壁之间的连接位置靠近结合齿轮215的一侧，且卡板204的底部与容纳腔室206的底部之间设置有弹性组件，弹性组件设置在靠近正向转动齿轮203的一侧。应注意的是，如图13至图15所示，本实施例中，设置在卡板204的底部与容纳腔室206的底部之间的弹性组件包括径向设置的弹簧208，容纳腔室206的底部形成有容纳孔，容纳腔室206的侧壁上沿着容纳孔的延伸方向形成有弧形凹槽，弹簧208的一端设置在容纳孔中，弹簧208的另一端通过弧形凹槽限位，且弹簧208的另一端与卡板204的端部的底部之间设置有端部直径大于杆部直径的半圆球销轴217。
如图13所示，卡板204的顶部形成有阶梯状的挡位面210，且各挡位面210的高度沿远离正向转动齿轮203的方向逐渐变低，应注意的是，本实施例中卡板204顶部的挡位面210为三个，分别为非超越正向挡位面、超越正向挡位面和反向挡位面，其中，靠近正向转动齿轮203的挡位面为反向挡位面，靠近结合齿轮215的挡位面为非超越正向挡位面，中间的为超越正向挡位面。
如图12所示，驱动轴202上套设有可移动的滑动组件211，滑动组件211的轴孔内沿抵靠在卡板204的挡位面210上，并能够在挡位面210上沿驱动轴202的轴向移动，以使卡板204的两个端部分别在正向转动齿轮203和结合齿轮215的轴孔中沿径向移动。
如图16和图17所示，结合齿轮215的轴孔内沿上的结合卡槽216的开 口朝向驱动轴202，结合卡槽216的形状由两部分组成，第一部分呈矩形(即开口段)，第二部分呈V形(即底壁)，卡板204上与结合卡槽216相对应的端部的形状与结合卡槽216的形状阴阳匹配。此外，结合齿轮215的轴孔内沿上设置有多个结合卡槽216，且相邻的结合卡槽216紧密相连，故而即使出现相邻结合卡槽216之间的尖部与卡板204端部的顶尖部相抵时，也可通过轻微的碰撞使两者之间自动相互让位而完成结合卡槽216与卡板204的顺畅啮合。
此外，本实施例中的卡槽205的形状及功能与第一实施例中类似，不再详述。
下面结合附图对本实施例的便于转向切换的可超越式传动装置中的“转向切换”操作进行描述：
当需要使输出齿轮201正向转动时。操作变档机构，使滑动组件211朝向结合齿轮215移动，也即，使滑动组件211的轴孔内沿抵靠在卡板204的顶面上靠近结合齿轮215的挡位面(非超越正向挡位面或超越正向挡位面)上。此时，卡板204的一个端部便可进入到正向转动齿轮203上的卡槽205中，而卡板204的另一个端部则与结合齿轮215上的结合卡槽216分离。由此，驱动轴202与正向转动齿轮203便扣合在一起，进而驱动轴202便可通过正向转动齿轮203带动输出齿轮201正向转动。
当需要使输出齿轮201反向转动时。操作变档机构，使滑动组件211朝向正向转动齿轮203的方向移动，也即，使滑动组件211的轴孔内沿抵靠在卡板204的顶面上靠近正向转动齿轮203的挡位面(反向挡位面)上。此时，卡板204的端部便可进入到结合齿轮215上的结合卡槽216中，而卡板204的另一个端部则与正向转动齿轮203上的卡槽205分离。由此，驱动轴202与结合齿轮215便扣合在一起，进而驱动轴202便可通过结合齿轮215、反向齿轮组212来带动输出齿轮201反向转动。
下面结合附图对本实施例的便于转向切换的可超越式传动装置中的“非超越”和“可超越”操作进行描述：
当滑动组件211的轴孔内沿位于卡板204上最靠近结合齿轮215的挡位面(非超越正向挡位面)上时，卡板204的一个端部完全进入到正向转动齿 轮203的卡槽205中(与第一实施例中类似)，另一个端部与结合齿轮215的结合卡槽216分离，此时，驱动轴202通过正向转动齿轮203带动输出齿轮201正向转动。如果在行驶过程中出现输出齿轮201的相对转速高于驱动轴202的转速，也即发生“超越”现象时，由于卡板204的一个端部完全进入到卡槽205中，便无法从卡槽205中移出，使得驱动轴202与正向转动齿轮203之间一直保持扣合状态。进而，输出齿轮201便会通过正向转动齿轮203和驱动轴202驱动发动机运转，进而迫使机动车减速并为机动车提供辅助制动，保证了在特殊情况下(如下坡时)机动车行驶的安全性。
当滑动组件211的轴孔内沿位于卡板204上中间的挡位面(超越正向挡位面)上时，卡板204的一个端部部分进入到正向转动齿轮203的卡槽205中(与第一实施例中类似)，另一个端部与结合齿轮215的结合卡槽216分离，此时，驱动轴202仍是通过正向转动齿轮203带动输出齿轮201正向转动。如果在行驶过程中出现输出齿轮201的相对转速高于驱动轴202的转速，也即发生“超越”现象时，由于卡板204的端部只是部分进入到卡槽205中，卡板204的端部便可从卡槽205中移出，使得驱动轴202与正向转动齿轮203之间的扣合解除。进而，输出齿轮201便会仅带动正向转动齿轮203接近零负荷转动，大大降低了机动车在“超越”滑行时惯性能量的损耗，同时也避免了发动机出现超怠速状况而浪费燃油。
如图18所示，其为本发明的第三实施例。
与上述第一实施例相比，本实施例中的主要区别点在于：卡板304自由设置在容纳腔室306中。下面仅就该区别点进行说明，与上述第一实施例相似的部分不再详述。
具体来说，卡板304与容纳腔室306之间为自由设置，也即，卡板304与容纳腔室306之间不相互连接。卡板304的一个端部活动设置在正向转动齿轮303的轴孔中，卡板304底部形成有导向圆柱，容纳腔室306的底面形成有容纳孔，导向圆柱与容纳腔室306的底面之间沿驱动轴304的径向设置有弹性组件(也即，弹簧308)，其中，弹簧308至少为两个，且分开设置，弹簧308的一端套箍在导向圆柱上，另一端插入到容纳孔中并与容纳孔底面相抵靠，由此可推动卡板304上活动设置在正向转动齿轮303的轴孔中的端 部沿正向转动齿轮303的径向移动，以插入到卡槽305中。
此外，本实施例中的其他结构及原理与上述第一实施例类似，在此不再详述。
如图19至图22所示，其为本发明的第四实施例。
如图19所述，便于快慢切换的可超越式传动装置用于驱动输出轴快速和慢速转动，包括输出轴401、驱动轴402和传动齿轮组等。其中，驱动轴402为输出轴401的转动提供动力；传动齿轮组至少为两套，且各套传动齿轮组传递的转速不同，用于实现输出轴401的快速和慢速转动；每套传动齿轮组中都包括相互啮合的主动齿轮和从动齿轮，主动齿轮套设在驱动轴402上，从动齿轮套设在输出轴401上，且主动齿轮与驱动轴402和从动齿轮与输出轴401中有一组为可结合与分离的。
如图20所示，本实施例中包括顺次设置的五套传动齿轮组。其中，第一套传动齿轮组中，从动齿轮412与输出轴401为可结合与分离的；第二套传动齿轮组中，主动齿轮421与驱动轴402为可结合与分离的；第三套传动齿轮组中，从动齿轮432与输出轴401为可结合与分离的；第四套传动齿轮组中，主动齿轮441与驱动轴402为可结合与分离的；第五套传动齿轮组中，从动齿轮452与输出轴401为可结合与分离的。应注意的是，本实施例中的第一套传动齿轮组可对应于一档，第二套传动齿轮组可对应于三档，第三套传动齿轮组可对应于四档，第四套传动齿轮组可对应于五档，第五套传动齿轮组可对应于二档
进一步，上述可结合与分离的齿轮与轴中，轴穿过齿轮的轴孔设置，齿轮的轴孔边缘形成有至少一个卡槽，轴上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿齿轮的径向往复移动，以插入到卡槽中或从卡槽中移出，实现轴与齿轮的结合与分离。
进一步，卡板在容纳腔室中沿轴的轴向设置，容纳腔室中设置有弹性组件，弹性组件与卡板端部的底部相抵靠，可推动卡板的端部沿齿轮的径向移动，卡板的顶部形成有阶梯状的挡位面，轴上套设有滑动组件，滑动组件的轴孔内沿抵靠在卡板顶部的挡位面上并可在阶梯状的挡位面上往复移动，以使卡板的端部沿齿轮的径向往复移动。
进一步，与上述第一实施例中类似，卡板的一端枢轴连接在容纳腔室的侧壁上，另一端活动设置在传动齿轮的轴孔中，弹性组件在容纳腔室中沿传动轴的轴向设置，弹性组件的端部与卡板上活动设置在传动齿轮的轴孔中的端部的底部相抵靠，可推动卡板的该端部沿传动齿轮的径向移动，以插入到卡槽中。具体来说，弹性组件包括弹簧，弹簧在容纳腔室中沿传动轴的轴向设置，弹簧的端部设置有鼓形滚珠，弹簧通过鼓形滚珠与卡板上活动设置在传动齿轮的轴孔中的端部的底部相抵靠。
进一步，本实施例中，第三套传动齿轮组中的主动齿轮431可作为第二套传动齿轮组和第四套传动齿轮组中的滑动组件；第二套传动齿轮组中的从动齿轮422可作为第一套传动齿轮组和第三套传动齿轮组中的滑动组件；第四套传动齿轮组中的从动齿轮442可作为第五套传动齿轮组中的滑动组件。
此外，本实施例中的其他结构及原理与上述第一实施例中类似，在此不再详述。
下面结合附图对本实施例的便于快慢切换的可超越式传动装置中的“快慢切换”和“可超越”操作进行描述：
第一套传动齿轮组的分离状态：第二套传动齿轮组中的从动齿轮422的轴孔内沿抵靠在第一套传动齿轮组中的卡板413的分离挡位面上，卡板413与第一套传动齿轮组中的从动齿轮412分离，即第一套传动齿轮组处于分离状态。
第一套传动齿轮组的超越结合状态：通过拔杈板403驱使第二套传动齿轮组中的从动齿轮422朝向第一套传动齿轮组中的从动齿轮412移动，并使从动齿轮422的轴孔内沿抵靠在卡板413的超越结合挡位面上，卡板413在弹簧作用力下向上旋转，卡板413与从动齿轮412部分结合，即第一套传动齿轮组处于超越结合状态。
第一套传动齿轮组的非超越结合状态：通过拔杈板403继续驱使第二套传动齿轮组中的从动齿轮422朝向第一套传动齿轮组中的从动齿轮412移动，并使从动齿轮422的轴孔内沿抵靠在卡板413的非超越结合挡位面上，卡板413在弹簧作用力下向上旋转，卡板413与从动齿轮412完全结合，即第一套传动齿轮组处于非超越结合状态。
第二套传动齿轮组的分离状态：第三套传动齿轮组中的主动齿轮431的轴孔内沿抵靠在第二套传动齿轮组中的卡板423的分离挡位面上，卡板423与第二套传动齿轮组中的主动齿轮421分离，即第二套传动齿轮组处于分离状态。
第二套传动齿轮组的超越结合状态：通过拔杈板404驱使第三套传动齿轮组中的主动齿轮431朝向第二套传动齿轮组中的主动齿轮421移动，并使主动齿轮431的轴孔内沿抵靠在卡板423的超越结合挡位面上，卡板423在弹簧作用力下向上旋转，卡板423与主动齿轮421部分结合，即第二套传动齿轮组处于超越结合状态。
第二套传动齿轮组的非超越结合状态：通过拔杈板404继续驱使第三套传动齿轮组中的主动齿轮431朝向第二套传动齿轮组中的主动齿轮421移动，并使从主动齿轮431的轴孔内沿抵靠在卡板423的非超越结合挡位面上，卡板423在弹簧作用力下向上旋转，卡板423与主动齿轮421完全结合，即第二套传动齿轮组处于非超越结合状态。
第三套传动齿轮组的分离状态：第二套传动齿轮组中的从动齿轮422的轴孔内沿抵靠在第三套传动齿轮组中的卡板433的分离挡位面上，卡板433与第三套传动齿轮组中的从动齿轮432分离，即第三套传动齿轮组处于分离状态。
第三套传动齿轮组的超越结合状态：通过拔杈板403驱使第二套传动齿轮组中的从动齿轮422朝向第三套传动齿轮组中的从动齿轮432移动，并使从动齿轮422的轴孔内沿抵靠在卡板433的超越结合挡位面上，卡板433在弹簧作用力下向上旋转，卡板433与从动齿轮432部分结合，即第三套传动齿轮组处于超越结合状态。
第三套传动齿轮组的非超越结合状态：通过拔杈板403继续驱使第二套传动齿轮组中的从动齿轮422朝向第三套传动齿轮组中的从动齿轮432移动，并使从动齿轮422的轴孔内沿抵靠在卡板433的非超越结合挡位面上，卡板433在弹簧作用力下向上旋转，卡板433与从动齿轮432完全结合，即第一套传动齿轮组处于非超越结合状态。
第四套传动齿轮组的分离状态：第三套传动齿轮组中的主动齿轮431的 轴孔内沿抵靠在第四套传动齿轮组中的卡板443的分离挡位面上，卡板443与第四套传动齿轮组中的主动齿轮441分离，即第四套传动齿轮组处于分离状态。
第四套传动齿轮组的超越结合状态：通过拔杈板404驱使第三套传动齿轮组中的主动齿轮431朝向第四套传动齿轮组中的主动齿轮441移动，并使主动齿轮431的轴孔内沿抵靠在卡板443的超越结合挡位面上，卡板443在弹簧作用力下向上旋转，卡板443与主动齿轮441部分结合，即第四套传动齿轮组处于超越结合状态。
第四套传动齿轮组的非超越结合状态：通过拔杈板404继续驱使第三套传动齿轮组中的主动齿轮431朝向第四套传动齿轮组中的主动齿轮441移动，并使从主动齿轮431的轴孔内沿抵靠在卡板443的非超越结合挡位面上，卡板443在弹簧作用力下向上旋转，卡板443与主动齿轮441完全结合，即第四套传动齿轮组处于非超越结合状态。
第五套传动齿轮组的分离状态：第四套传动齿轮组中的从动齿轮442的轴孔内沿抵靠在第五套传动齿轮组中的卡板453的分离挡位面上，卡板453与第五套传动齿轮组中的从动齿轮452分离，即第五套传动齿轮组处于分离状态。
第五套传动齿轮组的超越结合状态：通过拔杈板405驱使第四套传动齿轮组中的从动齿轮442朝向第五套传动齿轮组中的从动齿轮452移动，并使从动齿轮442的轴孔内沿抵靠在卡板453的超越结合挡位面上，卡板453在弹簧作用力下向上旋转，卡板453与从动齿轮452部分结合，即第五套传动齿轮组处于超越结合状态。
第五套传动齿轮组的非超越结合状态：通过拔杈板405继续驱使第四套传动齿轮组中的从动齿轮442朝向第五套传动齿轮组中的从动齿轮452移动，并使从动齿轮442的轴孔内沿抵靠在卡板453的非超越结合挡位面上，卡板453在弹簧作用力下向上旋转，卡板453与从动齿轮452完全结合，即第五套传动齿轮组处于非超越结合状态。
应注意的是，上述是以设有五套传动齿轮组为例来进行说明，但本发明并不局限于此，根据需要可以设有六套及以上套数的传动齿轮组，其原理同 上。此外，也可以将第一至第三实施例中的转向切换的结构应用于此，以便在同一装置中实现转向和快慢的切换。
如图19、图23至图26所示，其为本发明的第五实施例。
本实施例中的结构对应于上述第二实施例中的正向转动齿轮端，原理对应于上述第四实施例(仅有的区别是拔叉板的移动方向相反)，在此不再赘述。
如图19、图27至图30所示，其为本发明的第六实施例。
本实施例中的结构对应于上述第三实施例的正向转动齿轮端(仅有的区别是本实施例中的拔叉板移动方向与第三实施例中的滑动组件的移动方向相反)，原理对应于上述第五实施例，在此不再赘述。
本发明的便于切换的可超越式传动装置将两个直径相差过大而难于实现齿轮间错位滑入啮合的结构方式或爪与孔之间易发生抵触情况而难以实现齿孔结合的结构方式转换成了卡板与卡槽之间的插合、扣接，大大提高了切换的成功率和顺畅度。
此外，本发明的便于切换的可超越式传动装置通过卡板与卡槽的部分扣合，使得在出现“超越”现象时，可使传动轴与传动齿轮脱离开来，避免了“超越”运行状态下仍会消耗能源，以及惯性动能的过度损失；同时，本发明的便于切换的可超越式传动装置通过卡板与卡槽的完全扣合，使得在不需要或不允许“超越”运转时，可有效避免“超越”运转现象的发生，提高了运行的安全性。
应注意的是，上述是以机动车上的传动装置为例，对本发明的便于切换的可超越式传动装置进行详细说明。但应注意的是，本发明的便于切换的可超越式传动装置能够根据需要应用到任何具有传动装置的领域，如船舶、飞行器等，并不一定局限于下面所述的机动车领域。
以上借助具体实施例对本发明做了进一步描述，但是应该理解的是，这里具体的描述，不应理解为对本发明的实质和范围的限定，本领域内的普通技术人员在阅读本说明书后对上述实施例做出的各种修改，都属于本发明所保护的范围。

Claims (25)

  1. 一种便于切换的可超越式传动装置，其特征在于，包括传动齿轮和穿过传动齿轮轴孔设置的传动轴，传动齿轮的轴孔边缘形成有至少一个卡槽，传动轴的轴向上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿传动齿轮的径向往复移动，以插入到卡槽中或从卡槽中移出，实现传动轴与传动齿轮的结合与分离。
  2. 根据权利要求1所述的便于切换的可超越式传动装置，其特征在于，卡板在容纳腔室中沿传动轴的轴向设置，容纳腔室中设置有弹性组件，弹性组件位于卡板底面与容纳腔室底面之间，可推动卡板的端部沿传动齿轮的径向移动，卡板的顶部形成有阶梯状的挡位面，传动轴上套设有滑动组件，滑动组件的轴孔内沿抵靠在卡板顶部的挡位面上并可在阶梯状的挡位面上往复移动，以使卡板的端部沿传动齿轮的径向作有限制性的往复移动。
  3. 根据权利要求2所述的便于切换的可超越式传动装置，其特征在于，卡板的一端枢轴连接在容纳腔室的侧壁上，另一端活动设置在传动齿轮的轴孔中，弹性组件在容纳腔室中沿传动轴的轴向设置，弹性组件的端部与卡板上活动设置在传动齿轮的轴孔中的端部的底部相抵靠，可推动卡板的该端部沿传动齿轮的径向移动，以插入到卡槽中。
  4. 根据权利要求3所述的便于切换的可超越式传动装置，其特征在于，弹性组件包括弹簧，弹簧在容纳腔室中沿传动轴的轴向设置，弹簧靠近传动齿轮的端部设置有鼓形滚珠，弹簧通过鼓形滚珠与卡板上活动设置在传动齿轮的轴孔中的端部的底部相抵靠。
  5. 根据权利要求4所述的便于切换的可超越式传动装置，其特征在于，弹簧远离传动齿轮的端部设置有圆平头销轴，圆平头销轴的端部直径大于杆部直径，圆平头销轴抵靠在容纳腔室的端侧壁上，以保证弹簧作直线伸缩。
  6. 根据权利要求2所述的便于切换的可超越式传动装置，其特征在于，卡板的肩窝部枢轴连接在容纳腔室的侧壁上，一个端部活动设置在传动齿轮的轴孔中，弹性组件在容纳腔室中沿传动轴的径向设置，弹性组件的端部与卡板的端部的底部相抵靠，可推动卡板上活动设置在传动齿轮的轴孔中的端 部沿传动齿轮的径向移动，以插入到卡槽中。
  7. 根据权利要求6所述的便于切换的可超越式传动装置，其特征在于，弹性组件包括弹簧，弹簧在容纳腔室中沿传动轴的径向设置，弹簧的端部设置有端部直径大于杆部直径的半圆球销轴，弹簧通过半圆球销轴与卡板端部的底部相抵靠。
  8. 根据权利要求2所述的便于切换的可超越式传动装置，其特征在于，卡板自由设置在容纳腔室中，卡板的一个端部活动设置在传动齿轮的轴孔中，弹性组件在容纳腔室中沿传动轴的径向设置，弹性组件的端部与卡板端部的底部相抵靠，可推动卡板上活动设置在传动齿轮的轴孔中的端部沿传动齿轮的径向移动，以插入到卡槽中。
  9. 根据权利要求8所述的便于切换的可超越式传动装置，其特征在于，弹性组件包括弹簧，弹簧在容纳腔室中沿传动轴的径向设置，弹簧至少为两个，且分开设置，以维持卡板的平衡。
  10. 根据权利要求2所述的便于切换的可超越式传动装置，其特征在于，卡板顶部的阶梯状挡位面包括非超越结合挡位面和分离挡位面，滑动组件的轴孔内沿抵靠在非超越结合挡位面上时，卡板的端部完全插入到卡槽中，传动轴与传动齿轮非超越式结合；滑动组件的轴孔内沿抵靠在分离挡位面上时，卡板的端部从卡槽中移出，传动轴与传动齿轮分离。
  11. 根据权利要求10所述的便于切换的可超越式传动装置，其特征在于，卡板顶部的阶梯状挡位面还包括超越结合挡位面，滑动组件的轴孔内沿抵靠在超越结合挡位面上时，卡板的端部部分插入到卡槽中，传动轴与传动齿轮可超越式结合。
  12. 根据权利要求11所述的便于切换的可超越式传动装置，其特征在于，卡槽的开口朝向传动轴，且在传动轴的转动方向上前部深度大于后部深度，卡槽的底壁呈斜面状；卡板上活动设置在传动齿轮的轴孔中的端部的形状与卡槽的形状相配合，该端部的顶面呈斜面状，且斜面的形状和斜向与卡槽的底壁相一致。
  13. 根据权利要求12所述的便于切换的可超越式传动装置，其特征在 于，传动齿轮的轴孔边缘上均匀设置有多个卡槽，且相邻的卡槽之间设置有缓冲槽。
  14. 一种便于转向切换的可超越式传动装置，用于驱动输出齿轮正向和反向转动，其特征在于，包括：
    驱动轴，为输出齿轮的转动提供动力；
    正向转动齿轮，与输出齿轮相啮合，驱动轴与正向转动齿轮相结合可驱动输出齿轮正向转动；
    反向齿轮组，与输出齿轮相啮合，驱动轴与反向齿轮组相结合可驱动输出齿轮反向转动；
    驱动轴穿过正向转动齿轮的轴孔设置，正向转动齿轮的轴孔边缘形成有至少一个卡槽，驱动轴上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿正向转动齿轮的径向往复移动，以插入到卡槽中或从卡槽中移出，实现驱动轴与正向转动齿轮的结合与分离。
  15. 根据权利要求14所述的便于转向切换的可超越式传动装置，其特征在于，卡板在容纳腔室中沿驱动轴的轴向设置，容纳腔室中设置有弹性组件，弹性组件位于卡板底面与容纳腔室底面之间，可推动卡板的端部沿正向转动齿轮的径向移动，卡板的顶部形成有阶梯状的挡位面，驱动轴上套设有滑动组件，滑动组件的轴孔内沿抵靠在卡板顶部的挡位面上并可在阶梯状的挡位面上往复移动，以使卡板的端部沿正向转动齿轮的径向往复移动。
  16. 根据权利要求15所述的便于转向切换的可超越式传动装置，其特征在于，驱动轴上套设的滑动组件的外圆周上形成有结合齿，反向齿轮组的一端与输出齿轮相啮合，另一端可与滑动组件外圆周上的结合齿相互啮合或分离。
  17. 根据权利要求15所述的便于转向切换的可超越式传动装置，其特征在于，驱动轴上远离输出齿轮的一端套设有结合齿轮，反向齿轮组的一端与输出齿轮相啮合，另一端与结合齿轮相啮合；驱动轴穿过结合齿轮的轴孔设置，结合齿轮的轴孔内沿形成有至少一个结合卡槽，驱动轴中的卡板的另一端部可在容纳腔室中沿结合齿轮的径向往复移动，以插入到结合卡槽中或 从结合卡槽中移出，实现驱动轴与结合齿轮的结合与分离。
  18. 根据权利要求17所述的便于转向切换的可超越式传动装置，其特征在于，结合卡槽的开口朝向驱动轴，结合卡槽的形状由两部分组成，第一部分为开口段，呈矩形，第二部分为底壁，呈V形；卡板上与结合卡槽相对应的端部的形状与结合卡槽的形状阴阳匹配。
  19. 根据权利要求16或17所述的便于转向切换的可超越式传动装置，其特征在于，卡板顶部的阶梯状挡位面包括非超越正向挡位面和反向挡位面，滑动组件的轴孔内沿抵靠在非超越正向挡位面上时，卡板的端部完全插入到正向转动齿轮上的卡槽中，驱动轴与正向转动齿轮非超越式结合；滑动组件的轴孔内沿抵靠在反向挡位面上时，卡板的端部从正向转动齿轮上的卡槽中移出，驱动轴与正向转动齿轮分离，并与反向齿轮组结合。
  20. 根据权利要求19所述的便于转向切换的可超越式传动装置，其特征在于，卡板顶部的阶梯状挡位面还包括超越正向挡位面，滑动组件的轴孔内沿抵靠在超越正向挡位面上时，卡板的端部部分插入到正向转动齿轮上的卡槽中，驱动轴与正向转动齿轮可超越式结合。
  21. 一种便于快慢切换的可超越式传动装置，用于驱动输出轴快速和慢速转动，其特征在于，包括：
    驱动轴，为输出轴的转动提供动力；
    至少两套传动齿轮组，各套传动齿轮组传递的转速不同，用于实现输出轴的快速和慢速转动；
    每套传动齿轮组中都包括相互啮合的主动齿轮和从动齿轮，主动齿轮套设在驱动轴上，从动齿轮套设在输出轴上，且主动齿轮与驱动轴和从动齿轮与输出轴中有一组为可结合与分离的；
    可结合与分离的主动齿轮与驱动轴或从动齿轮与输出轴中，轴穿过齿轮的轴孔设置，齿轮的轴孔边缘形成有至少一个卡槽，轴上形成有容纳腔室，容纳腔室中设置有卡板，卡板的端部可在容纳腔室中沿齿轮的径向往复移动，以插入到卡槽中或从卡槽中移出，实现轴与齿轮的结合与分离。
  22. 根据权利要求21所述的便于快慢切换的可超越式传动装置，其特 征在于，卡板在容纳腔室中沿轴的轴向设置，容纳腔室中设置有弹性组件，弹性组件位于卡板底面与容纳腔室底面之间，可推动卡板的端部沿齿轮的径向移动，卡板的顶部形成有阶梯状的挡位面，轴上套设有滑动组件，滑动组件的轴孔内沿抵靠在卡板顶部的挡位面上并可在阶梯状的挡位面上往复移动，以使卡板的端部沿齿轮的径向往复移动。
  23. 根据权利要求22所述的便于快慢切换的可超越式传动装置，其特征在于，包括顺次设置的五套传动齿轮组，
    第一套传动齿轮组中，从动齿轮与输出轴为可结合与分离的；
    第二套传动齿轮组中，主动齿轮与驱动轴为可结合与分离的；
    第三套传动齿轮组中，从动齿轮与输出轴为可结合与分离的；
    第四套传动齿轮组中，主动齿轮与驱动轴为可结合与分离的；
    第五套传动齿轮组中，从动齿轮与输出轴为可结合与分离的；
    其中，第三套传动齿轮组中的主动齿轮可作为第二套传动齿轮组和第四套传动齿轮组中的滑动组件；
    第二套传动齿轮组中的主动齿轮可作为第一套传动齿轮组和第三套传动齿轮组中的滑动组件；
    第四套传动齿轮组中的主动齿轮可作为第五套传动齿轮组中的滑动组件。
  24. 根据权利要求22所述的便于快慢切换的可超越式传动装置，其特征在于，卡板顶部的阶梯状挡位面包括非超越结合挡位面和分离挡位面，滑动组件的轴孔内沿抵靠在非超越结合挡位面上时，卡板的端部完全插入到齿轮上的卡槽中，轴与齿轮非超越式结合；滑动组件的轴孔内沿抵靠在分离挡位面上时，卡板的端部从齿轮上的卡槽中移出，轴与齿轮分离。
  25. 根据权利要求24所述的便于快慢切换的可超越式传动装置，其特征在于，卡板顶部的阶梯状挡位面还包括超越结合挡位面，滑动组件的轴孔内沿抵靠在超越结合挡位面上时，卡板的端部部分插入到齿轮上的卡槽中，轴与齿轮可超越式结合。
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CN106717661A (zh) * 2016-11-27 2017-05-31 苏州君丰辰电子科技有限公司 联动切换装置
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CN205086678U (zh) 2016-03-16
PE20171494A1 (es) 2017-10-18
EP3176067A1 (en) 2017-06-07
CN105059109A (zh) 2015-11-18
CN105059109B (zh) 2017-11-14
PH12017500187A1 (en) 2017-06-28
AP2017009789A0 (en) 2017-02-28
EA201700092A1 (ru) 2017-11-30
US20170219074A1 (en) 2017-08-03
CO2017002077A2 (es) 2017-05-31
MA40549A (fr) 2016-02-04

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